High energy impact forming machine



Aug. 25, 1964 J. K. MUREK ETAL HIGH ENERGY IMPACT FORMING MACHINE 6Sheets-Sheet 1 Filed April 26, 1962 Cfimziopizer Zezlefga,

Aug. 25, 1964 J. K. MUREK ETAL 3,145,648

HIGH ENERGY IMPACT FORMING MACHINE Filed April 26, 1962 6 Sheets-Sheet 2INVENTORS 4 T jsefflflar ek 6km50fier 222527 940 g 04;; 75%,, was, W

Aug. 25, 1964 J. K. MUREK ETAL HIGH ENERGY IMPACT FORMING MACHINE 6Sheets-Sheet 3 Filed April 26, 1962 Z; TM 3 Aug. 25, 1964 Filed April26, 1962 J. K. MUREK ETAL HIGHENERGY IMPACT FORMING MACHINE 6Sheets-Sheet 5 W INVENTORS 04W, 7% wi 25, 1964 J. K. MUREK ETAL3,145,648

HIGH ENERGY IMPACT FORMING MACHINE Filed April 26, 1962 6 Sheets-Sheet 68 INVENTOR-S ikmmk 110 535 Cmi'z gver Zeale ga/ 0km, 7W

United States Patent 3,145,648 HIGH ENERGY IMPACT FORMING MACHINE JosefKarl Mun-eh, San Diego, Calif, and Christopher Zeilenga, Chicago, Ill.,assignors to Trans Energy Corp., New York, N.Y., a corporation ofDelaware Filed Apr. 26, 1962, Ser. No. 190,359 17 Claims. ((11. 100-264)The present invention relates to a novel high energy rate Or highvelocity impact forming or workpiece processing machine.

It is contemplated that a machine incorporating features of the presentinvention will include substantially sealed high fluid pressure chambermeans providing fluid under pressure for driving a ram or the likethrough a working stroke at a high velocity. The high velocities andenergies encountered in such a machine impose great stresses on themachine so that substantial problems of reliability and machine life areencountered.

After each working stroke of the ram it is necessary to return or recockthe ram against the force of the fluid under pressure which bearsagainst the ram. Additional substantial problems have been encounteredin providing a structure capable of accommodating the forces andstresses involved during recocking and subsequent retention of the ramwhile, at the same time, capable of functioning rapidly and reliably.

An important object of the present invention is to provide a novelmachine of the above described type having improved strength, ruggednessand reliability.

A further object of the present invention is to provide a novelapparatus of the above described type which incorporates means forresetting or recocking the ram of the apparatus, which means is capableof functioning rapidly and reliably and has an improved working life.

Still another important object of the present invention is to provide anovel high energy impact forming machine of the above described typehaving means for resetting or recocking the ram constructed andsupported with respect to a main frame of the apparatus in a. mannerwhich enables the recocking means to be effectively and substantiallyisolated from the remainder of the apparatus at the instant of impact ofthe ram against a work structure so as to minimize or substantiallyelimimate a transfer of impact and inertia stresses and loads betweenthe recocking means and the remainder of the apparatus whereby to reduceany possibility of injury to the apparatus.

Other objects and advantages of the present invention will becomeapparent from the following description and the accompanying drawings,wherein:

FIG. 1 is a front elevational view showing an apparatus incorporatingfeatures of the present invention;

FIG. 2 is a side elevational view of the apparatus shown in FIG. 1;

FIG. 3 is an enlarged sectional view of a main frame member of theapparatus taken generally along line 3-3 in FIG. 2;

FIG. 4 is an enlarged fragmentary partial sectional view taken generallyalong line 44 in FIG. 2;

FIG. 4a is an enlarged fragmentary partial sectional View takengenerally along line ta-4a in FIG. 2 and provides an extension of FIG.4;

FIG. 5 is a sectional view taken along line 5-5 in FIG. 4;

FIG. 6 is an enlarged fragmentary sectional view similar to a portion ofFIG. 5 and shows the structure for I guiding a corner of the ram ingreater detail; and

FIG. 7 is a schematic diagram showing hydraulic and electrical actuatingand control means for the apparatus.

Referring now more specifically to the drawings Wherein like parts aredesignated by the same numerals throughout the various figures, anapparatus 10 incorporating features of the present invention is shown inFIGS. 1 and 2. The apparatus comprises a main frame structure or casting12 which is preferably formed substantially in one piece, as will bedescribed more in detail below. The main frame structure or casting isprovided with a substantially spherical head portion 14 which is sealedand adapted to contain air or other suitable gas under high pressure. Aram 16 is telescopically associated with the spherical head portion 14and is adapted to be actuated by the fluid or gas under pressure througha downward or Work stroke. The rain is provided with an elongated shankportion 18 slidably extending through an opening at the lower end of thespherical head portion. The trailing shank portion 18 of the ram mergeswith an enlarged head portion 20, which is adapted to carry a suitableworkpiece processing die 22.

The main frame structure or casting 12 is provided with a relativelyheavy base portion 24 which is suitably supported above a fixed floor26. The frame head and base portions 14 and 24 are integrally connectedby pairs of upstanding side or corner portions 28-30 and 32-34 as shownin FIGS. 1-3 and 5. These upstanding corner or side portionsrespectively gradually increase in transverse cross-section and weightfrom their upper ends toward integral junctions with the base portion24.

In accordance with a feature of the present invention, the junctionsbetween the side or corner portions and the base portion 24 are formedso as to minimize any concentration of stresses at such junctions duringworking of the machine whereby to reduce any possibility of injury tothe machine. In this connection, it is to be noted that the base portion24 is formed with a substantially semicylindrical seat 36 which extendsbetween the opposite pairs of side or corner portions 28-30 and 32-34.As shown best in FIGS. 1 and 3, the semicylindrical surface or seat 36is formed so that it merges with the lower ends of the opposite side orcorner portions so as to eliminate sharp corners between the cornerportions and the base portion of the frame structure. It is also to benoted that the surface of the base portion 24 which extends directlybetween the lower ends of the corner portions 32 and 34 is in the formof an arcuate surface 40 as shown in FIGS. 2 and 3. It is to beunderstood that the upper surface of the base portion is similarlycurved between the lower ends of the corner portions 28 and 30, as shownat 41 in FIG. 3.

As shown in FIGS. 1 and 4a, a substantially semicylindrical solid pad 42is disposed on the seat 36. The pad presents a horizontal upper surface44 on which a work structure or die 46 to be processed may be disposed.A bolt 48 extends through an aperture provided in the base portion 24and is connected with the pad 42 for drawing the pad firmly against theseat 36. The semicylindrical pad 42 and the seat 36 are formed withaccurately finished complementary surfaces. Thus, when an impact load isimposed on the pad 42 during a working stroke of the ram, the pad 42will tend to distribute the load and the resulting stresses radially andgenerally uniformly over the seat 36. As a result, stress concentrationsin the main frame of the machine are minimized and injury to the machineis avoided and its working life is increased.

As shown best in FIG. 5, the head portion 2d of the ram 16 is generallyrectangular. Corners of the ram head portion are retained and supportedby vertical guide elements 50, 52, 54 and 56 which are respectivelysecured to the upstanding corner or side portions 28, 30, 32 and 34 ofthe frame structure. These elements extend for guiding the lower end ofthe ram as the ram moves be tween the upper or cocked position, shown inFIG. 1,

and a lower or work engaging position. As previously indicated, the ramis adapted to be driven downwardly at a high velocity by means of air orgas under pressure within the chamber portion 14 of the frame structureso as to accomplish processing or forming of a workpiece with a highvelocity, high energy impact force.

In order to rccock and releasably retain the ram, the machine isprovided with means 58 which is adapted to be moved between raised andlowered positions and to be releasably interconnected with the headportion 20 of the ram. The recocking and control means 58 comprises ayoke or casting 60 which encircles the main frame or casting 12, asshown best in FIG. 5. Rollers 62, 64, 66 and 68 are bounded on the yokeor casting 61 respectively, for engagement with vertical side or guidesurfaces presented by the upstanding corner portions 28, 3t), 32 and 34of the main frame structure. The casting 60 is thus supported and guidedfor vertical movement relative to the main frame structure.

The recocking means 58 includes latch means carried by the casting 60,as shown best in FIGS. 4 and 5, and releasably engageable with the headportion 20 of the ram. This latch means comprises a first pair of links7% and 72 pivotally mounted on the casting 61 by a pin 74 at one side ofthe ram, and a pair of essentially identical links 76 and 78 pivotallycarried by a pin 86 at the opposite side of the ram. Rods 82 and 84respectively extend between the pairs of links 7072 and 76-78, whichrods rotatably carry elongated star wheels 86 and 88. These star wheelsare formed with circumferentially spaced elongated grooves which arearcuately formed for accommodating rounded bosses 90 and 92 formedintegrally with the opposite margins of the ram head portion 20. It willbe observed that when the star wheels are supported by their respectivelink structures in the positions shown in FIG. 4, they engage beneaththe rounded bosses 90 and 9 2 of the ram structure, which bosses conformto and are fully seated within a pair of grooves of the star wheelswhereby the star wheels are effectively locked against rotation abouttheir own axes.

When it is desired to release the ram, the link structures supportingthe star wheels are pivoted in opposite directions so that the starwheels are shifted laterally outwardly away from the bosses 9t? and 92.This immediately causes partial disengagement of the bosses from thearcuate seats on the star wheels and the star wheels are no longerlocked against rotation about their own axes. Thus, as the star wheelsare shifted laterally outwardly with their linkage structures, they alsobegin to rotate about their own axes under the pressure exerted by theram until the movement of the star wheels has been sufficient completelyto release the ram for its downward or working stroke. This rollingcontact between the ram and the latch elements or star wheels greatlyminimizes wear between these parts and reduces maintenance on themachine.

In order to control the latch elements of the recocking mechanism,hydraulic or fluid pressure cylinders 94 and 96 are provided in thecasting 60 at opposite sides of the ram. Pistons 9S and 100 are operablein these cylinders, which pistons are secured to rods 192 and 104 havinghook portions 106 and 1618. The book portion 106 engages over a bar 110extending between and connected to upper end portions of the links 70and 72, while the hook portion 108 engages over and is connected to abar 112 which extends between upper end portions of the links 76 and 78.It will be appreciated that by controlling the operation of thehydraulic cylinders 94 and 96, in a manner which will be described morefully below, the latch elements may be actuated for engagement with ordisengagement from the ram.

As previously indicated, the pressure chamber 14 is sealed so that thegas therein is always maintained under a high pressure which might, forexample, be on the order of 2000 p.s.i. Thus, when the ram is in theraised or cocked position, there will always be a great force biasingthe ram downwardly regardless of whether or not the machine is in use orbeing attended to by an operator. Therefore, the machine is providedwith means for releasably locking the latch elements so as to precludeany possibility of the latch elements accidentally becoming disengagedfrom the ram as a result, for example, of a failure in the hydraulicsystem controlling the cylinders 94 and 96.

The safety or locking means comprises hydraulic or fluid pressurecylinders 114 and 116 formed in the casting 60 beneath the cylinders 4and 96. A piston 118 is slidably mounted in the cylinder 114 and isadapted to be actuated by fluid or hydraulic pressure toward the left asviewed in FIG. 4. A similar piston 12% is dispose in the cylinder 116and is adapted to be actuated by fluid or hydraulic pressure outwardlyor toward the right, as viewed in FIG. 4. Outer ends of the pistons 118and 129 are respectively connected to transverse or yoke members 122 and124. As shown in FIGS. 4 and 5, opposite ends of the transverse member122 are respectively secured to outer ends of rods 126 and 128.Identical rods 13% and 132 are connected with the transverse or crossmember 124.

As shown best in FIG. 5, the rods 126 and 128 extend through suitableguideways formed in the casting at opposite sides of and parallel to thecylinder 114. The rods 130 and 132 slidably extend through similarguideways at opposite sides of the cylinder 116. Inner ends of the rods126 and 128 are threadedly or otherwise suitably connected to atransverse stop or latch bar 134 which is adapted to slide along andbear against abutment surfaces 136 and 138 formed on the casting. Asshown in FIGS. 4 and 5, the bar 134 is adapted to be positioned beneathlaterally extending stop or abutment portions 140 and 142 of the links70 and 72. The latch or stop bar 134 is thus adapted to prevent thelinks '71) and 72 from pivoting in a counterclockwise direction, asviewed in FIG. 4, so as to preclude release of the ram when the latchbar is in the position shown. A substantially identical transversemember or latch bar 144 is connected to inner ends of the rods 130 and132 and is slidable on surfaces 146 and 148 between the extendedposition shown in FIGS. 4 and 5 and a retracted position. The bar 144 isalso adapted to engage beneath abutment portions 159 and 152 of thelinks 76 and 78 for locking the links against clockwise pivotalmovement, as viewed in FIG. 4.

The stop or latch bars 134 and 144 are normally biased toward theirextended or link locking positions by compression springs 154, 156, 153and 160, respectively disposed around the rods 126, 128, 130 and 132.The arrangement of the pistons in the cylinders 114 and 116 is suchthat, when fluid under pressure is directed into the cylinders, thepistons are shifted outwardly for moving the bars 134 and 144 from theirextended or locking positions shown outwardly in opposite directionssufiiciently to preclude engagement with the projecting abutmentportions of the links. Preferably the locking or latch bars are operatedso that they will be withdrawn one at a time, in the manner describedmore fully below, for providing a further safety factor precludingaccidental discharge of the ram.

The recocking and locking casting or frame member 60 is supported andadapted to be actuated for enabling it to be lowered from the positionshown in FIGS. 1, 2 and 4 after the ram has been released for movementdownwardly through a working stroke. The arrangement is such that themember 61} may be moved to a lowered position at which the latchelements 86 and 83 may be reengaged with the ram, whereupon the member60 may be raised for lifting the ram to its elevated or recockedposition.

In order to support and actuate the member 60, vertically disposedhydraulic or fluid pressure cylinders 162 and 164 are formed integrallywith the casting 60. Hollow piston structures 166 and 168 arerespectively associated with the cylinders 162 and 164. As shown best inFIG. 4a, the piston structure 166 comprises a first tubular member 170having an upper end portion slidably disposed within the cylinder 162and having a lower end portion telescopically receiving and welded orotherwise fixed to an upper end portion of a second tubular member 172.A lower end of the piston member 170 is adapted to engage and rest on anannular abutment surface 174.provided on the base portion of the mainframe while the piston member 172 slidably extends through a verticalbore 176 provided in the base portion of the main casting. A sleevebearing 173 is disposed on the portion of the tubular member 172extending through the bore 176 for facilitating sliding movement of thetubular piston member 172 relative to the base portion of the main framemember. The bearing sleeve is retained between an annular shoulder 180formed on the tubular member 172 and a collar 182 fixed on the tubularmember beneath and spaced from the bottom surface of the main framemember.

A lower end portion of the tubular piston member 172 extends into and isslidable relative to a tubular fitting 184 which is suitably secured tothe floor 26 or other support surface. The tubular fitting 184- isprovided with openings or" ports 186 and 187 adapted to be connectedwith conduits ofa hydraulic system described in detail below. The ports186 and 187 communicate with an annular chamber 188 within the fittting184, which chamber in turn communicates with a port 1% formed in thewall of the tubular piston 172. The lower end of the piston 172 is, ofcourse, closed and sealed by a plug 192, and annular packing and sealmeans 194 and 196 are provided above and below the annular chamber 188for sealing the chamber while permitting the piston mem her 172 to sliderelative to the fitting 184. With this structure, hydraulic fluid may bedelivered under pressure to or discharged from the cylinder 162 byflowing through the ports 186, 187 and 190 and the hollow or turbularpiston members 170 and 1.72.

The hollow piston structure 168 is identical to the piston structure 166and, therefore, need not be described in detail. It suflices to statethat the piston structure 168 comprises tubular members 198 and 200corresponding to the previously described tubular piston memof ahydraulic control system.

In FIG. 7 a hydraulic and electrical control system included in theapparatus is shown in simplified anddiagrammatic form. This controlsystem comprises a hydraulic pump 21% which is constantly driven by asuitable electric motor or any other prime mover. The pump 210 has itsinlet side connected by conduit means 212 with a reservoir 214 through acooler 216 of known construction. An outlet port of the pump isconnected with a pressure conduit 218. Preferably a pressure reliefvalve 220 is connected between the pressure line and the reservoir forreturning any excess fluid to the reservoir.

In the embodiment shown the pressure line 218 is connected with a port222 of a spring offset single solenoid four-way valve 224. The valve 224has a second port 226 connected with a conduit 228 and another port 230connected with a conduit 232. The valve is spring biased so as normallyto interrupt communication between the port 222 and the port 226 whileconnecting the port 226 to the port 230. The solenoid 232 is providedfor actuating the valve so as to connect the port 222 with the port 226and direct fluid under pressure to the conduit 228.

The conduit 228 is connected by suitable branch conduits 234 and 236with the lock cylinder 114. In addition the conduit 228 is connectedthrough a check valve 238, permitting flow in one direction, with afirst port 240 of a mechanically operated four-way valve 242 associatedwith the cylinder 114. As indicated in FIG. 7, the valve 240 ismechanically interconnected with the piston 113 so as to be operated inresponse to movement of the piston 113.

The valve 242 includes another port 244 connected with the conduit 228through a check valve 246 permitting flow in a direction opposite to theflow through check valve 238. Still another port 248 of the valve 242 isconnected by a conduit 250 with the lock cylinder 116. The piston in thecylinder 116 is also mechanically interconnected with another valve 252which serves to control the operation of the latch cylinders 94 and 96in a manner to be described.

The valve 252 is adapted to be actuated in one direction by themechanical linkage with the piston 120, and to be operated in theopposite direction by a pilot 254. The valve 252 is provided with apressure inlet port 256 connected with the pressure conduit 218 bysuitable branch conduits 258 and 260. Preferably a check valve 262 isconnected in the conduit 260 so as to minimize any possibility ofreverse flow of fluid from the latched cylinders in the event of afailure of the pump.

The valve 252 includes a second port 264 connected with first ends ofthe latch cylinders 94 and 96 by a'conduit 266 and suitable branchconduit means 268. Opposite ends of the cylinders 94 and 96 areconnected with another port 270 of the valve 252 by a conduit 272 andsuitable branch conduit means 274. An outlet port 276 of the valve 252is connected by conduit means 278 with the reservoir 214 through aspring biased pressure relief valve 280.

The apparatus includes an electrical control and relay panel 281electrically connected by Wires 283 and 285 with suitable power linesL-l and L2. This panel is also connected by wires 287 and 289 with thesolenoid 232. The control panel includes a relay for controlling thesolenoid 232, which relay is adapted to be manually actu. ated upon thedepression of a start button 291.

The portion of the hydraulic and electrical control means thus fardescribed serves to control the operation of the latch cylinders 94 and96 and the locking cylinders 114 and 116 in the following manner. It isassumed that the apparatus is in an idle condition with the ram 26latched and locked in its elevated position. When the machine is in thiscondition, the solenoid 232 is deenergized so that the pressure port 222of the valve 224 is disconnected from the port 226. At the same time thevalve 242 is conditioned so that the port 240 is disconnected from theport 243, and the valve 252 is positioned so that the port 256 isconnected to the port 264, while the port 270 is connected with the port276. In other words, the valves are conditioned so that hydraulic fluidunder pressure is blocked from the latching cylinders 114 and 116, whilethe fluid under pressure is directed to the outer ends of the latchcylinders 94 and $6.

In order to actuate the apparatus, the start button 292 is manuallydepressed so that the solenoid 232 is energized for shifting the valve224 to connect the port 222 with the port 226. Hydraulic fluidunderpressure is then directed to the locking cylinder 114 for shifting thepiston 118 to disengage the locking element associated therewith fromthe links of the latching means. Upon substantial completion of themovement of the piston 11%, the valve 242, which is mechanically linkedwith the piston, is actuated for connecting the port 240 with the port248 so that hydraulic fluid under pressure is directed to the lockingcylinder 116 The locking element associated with the piston 120 is thenretracted from the latch means as the piston is shifted by the fluidunder pressure. It is to be noted that with this arrangement the piston120 is actuated only after the piston 118' has been actuated whereby adouble safety is provided. When the piston 12% has withdrawn itsassociated locking element from the latch means, the mechanicalinterlock between the piston 120 and the valve 252 causes the valve tobe actuated for connecting the port 256 with the port 275 and the port264 with the port 276. When this occurs, fluid under pressure isdirected to the cylinders 94 and 96 for causing the latch means to beretracted, whereby to release the ram. At the same time fluid is forcedfrom the outer ends of the cylinders 94 and 96 and down through theconduits 265 and 278.

In addition to the previously described means for controlling andactuating the latching cylinders and the look ing cylinders, the systemcomprises means for controlling and actuating the cylinders 162 and 164in the recocking slide or frame member 69. This means includes a springcentered four-way valve 282 adapted to be actuated in oppositedirections by solenoids 284 and 286 and having a pressure inlet port 288connected with the pressure conduit 258 by a branch conduit 290. Thevalve 282 has another port 292 connected by conduits 294 and 296 withthe main ports 186 and 2% of the fittings 184 and 2% through main checkvalves 298 and 300, respectively. These check valves are of knownconstruction and normally permit flow only into the ports 1% and 208.However, these check valves are of a type including pressure actuateddevices 362 and 304 which are adapted to be operated for unseating oropening the check valves 2% and 300 for permitting reverse flow of thehydraulic fluid.

The valve 282 includes a third port 3% connected by conduits 3G8 and 310with the pilot or actuating devices 362 and 394 of the check valves 29?and 306. The structure of the valve 282 is such that the port 306 isnormally in communication with the port 292 and with a drain port 312when the valve 282 is centered, while at the same time the pressureinlet port 238 is blocked. The drain port312 is connected by a suitableconduit 314 with the reservoir.

The additional ports 187 and 189 of the fittings 184 and 2%,respectively, are connected with check valves 32d and 322 having outletsconnected with the reservoir through conduits 324 and 326. These checkvalves are of known construction and are normally closed to prevent theflow of hydraulic fluid therethrough. These valves are similar to thepreviously described check valves in that they include pressure operatedactuating or pilot devices 328 and 33% which are adapted to be operativefor opening the check valves 32% and 322 for permitting fluid to drainfrom the cylinders 162 and 164. Fluid under pressure is provided foroperating the devices 328 and 338 through conduit 332 which is connectedwith the previously described conduit 278 by a branch conduit 334. Withthis arrangement it is to be noted that, when the latch cylinders 94 and96 are actuated for releasing the ram and for forcing fluid underpressure from their outer ends and down through the conduit 278, aportion of the fluid under pressure will be delivered to the devices 323and 33a? for opening the check valves 32% and 322, whereby fluid startsto drain from the cylinders 162 and 164 while permitting the recockingcasting or frame member 6%) to move from its fully raised positiontoward a lowered position. It will be appreciated that the spring biasedpressure relief valve 280 is such as to maintain the desired pressurefor enabling the check valves to be opened, and, if desired, a suitabletime delay device 336 may be interconnected with the pressure reliefvalve for preventing the valve from opening prematurely.

It is important to note that, when the ram 16 is released and startsaccelerating rapidly downwardly, a reaction force is provided whichcauses the main frame 12 of the machine and all of the pants fixedthereto, or supported thereby, to start to move upwardly. Since the massof the main frame and its related components is much larger than that ofthe ram, the length of travel of the main frame and the componentssupported thereby is quite small as compared with that of the ram at theinstant of impact of the ram against the Work structure supported on thebase of the main frame.

The masses of the ram and the main frame with its connected componentsare related to each other so that the inertia of the upwardly movingmain frame will be suflicient to offset the inertia and impact forcesprovided by the downwardly moving ram at the moment of impact. With thisarrangement the machine needs no heavy supporting floors or otherstructure since substantially all of the stresses and shock loads areabsorbed within the machine itself.

As previously indicated, everything fixed to or supported by the mainframe begins to move upwardly immediately upon downward movement of theram. This includes the recocking frame or slide member 60 and itsassociated mechanism, which initially is supported on the main framethrough the piston structures 166 and 168 and the columns of hydraulicfluid under pressure within these piston structures and the associatedcylinders 162 and 164. However, it is to be noted that upwardacceleration of the recoclcing frame 60 is minimized by the previouslydescribed control circuit means which causes the check valves 32% and32.2 to open for permitting fluid to drain from the cylinders 162 and164 substantially immediately after the release of the ram. Thearrangement is such that, at the instant of ram impact, the recockingframe tl is no longer mechanically or hydraulically supported on themain frame. Furthermore, since the piston structures 166 and 168 areslidable relative to the main frame, in the manner previously described,the recocking frame 60 is free to float in space substantiallyindependently of the main frame at the moment of ram impact. Thus, theram does not serve to stop any upward movement of the recocking frame 60as it does serve to stop the upward movement of the main frame, and anyinertia forces which may be provided by the recocking frame are notimposed on the main frame of the machine or the ram, whereby to minimizeany possibility of injury to the main frame as a result of impact andinertia forces which must be absorbed thereby.

In order to decelerate the recocking frame 60 and its associatedmechanism, which, as indicated above, is effectively disconnected fromthe main frame at the moment of ram impact, dashpot devices 338 and 340are connected with opposite sides of the frame member 60 as shown inFIGS. 1, 2 and 4d. Each of these devices comprises a cylinder 342 havinga piston slidable therein and connected by means of a rod 344 with theframe 60. The devices may utilize known constructions for providingresistance to the movement of the piston within the cylinder 342 forproviding the desired braking eflect. Since the acceleration of therecocking frame 60 is minimized by releasing the fluid within thecylinders 162 and 164 in the manner described above, the deceleration ofthis frame member may be readily controlled by the devices 3 33 and 340which have their lower ends fixed to the floor or any other suitablesupport structure separate from the main frame of the machine.

Referring again to FIG. 7, it is seen that the control system includes alimit switch 346 adapted to be engaged and closed by a dog 348 carriedby the recocking frame when the recocking frame has moved from itsraised position to a lowered position at which the latch means may againbe engaged with the ram. The limit switch is suitably connected with thepower lines L-l and L-2 and with a solenoid 356 by wires 352 and 354.The solenoid is associated with and adapted to control a spring biasedvalve 356 having a first port 358 connected with 9 the hydraulicpressure line 258 by a branch conduit 360.

The valve 356 includes another port 362 connected with the conduit 278by a branch conduit 364, a third port 366 connected with the pilotdevice 254 of the valve 252 by a conduit 368, and still another port 370connected with the reservoir by a conduit 372.

The valve 356 is spring biased so that, when the solenoid 350 isdeenergized, the ports 358 and 362 are blocked and the port 366 isconnected with the drain port 37 0. When the recocking mechanism hasreached its lowermost position and the limit switch 346 is closed, thesolenoid 350 is deenergized and the valve 356 is shifted for connectingthe port 358 with the port 366, and the port 362 with the drain port370. Hydraulic fluid under pressure is then directed to the pilot device254 for shifting the valve 252 in a manner which causes the cylinders 94and 96 to be operated for reengaging the latch means with the ram. Atthe same time, fluid forced from the inner ends of the cylinders 94 and96 is directed through the conduits 270 and 278 to the reservoir throughthe valve 356. Since the conduit 278 is connected directly with thereservoir through the valve 356, the pressure on the check -valvecontrol devices 328 and 330 is relieved so that the check valves 320 and322 are closed. The limit switch 346 is also connected by wires 374 and376 between the power supply and a relay in the con- .trol panel 281which is connected by wires 391 and 393 with a solenoid 378 associatedwith a spring biased valve 380. The valve has a normally blocked inletport 382 connected by conduit 384 with a conduit 386 that is in turnconnected to the port 230 of the valve 224. The -valve'380 also has adrain port 388 connected with the reservoir by suitable conduit 390. Thecontrol panel 281 is wired so that the starting relay therein is alsooperatively connected with the limit switch 346. The arrangement is suchthat when the limit switch 346 is closed, the starting relay is actuatedso that the solenoid 232 is deenthe limit switch 394 is closed whereuponrelay means in the control panel 281 is operated for deenergizing thesolenoid 378.

The limit switch 394 is suitably connected to an associated relay in thecontrol panel by wires 395 and. 397, which relay is connected by meansof wires 396 and 398 with the solenoid 284 associated with the valve282.

When the switch 394 is closed, the solenoid 284 is energized forshifting the valve 282 to connect the inlet port 238 with the port 292for directing fluid under pressure through the check valves 298 and 300and into the cylinders 162 and 164 for raising the recocking mechanismwhich, as explained above, has already been reengaged with the ram.

When the recocking mechanism reaches its uppermost position, the dog 348engages and actuates a limit switch 400 which is suitably connected bywires 402 and 404 with 'the relay and'control panel 381 for deenergizingthe solenoid 284 so that the valve 282 is shifted for blocking the inletport 288.

It is contemplated that under certain circumstances it may be desirablemanually to control raising of the recocking mechanism. This may beaccomplished by providing the relay or control panel 281 with a switchsuitably electrically connected with the solenoid 284 and manuallyoperable by a push button 406. In order to preclude any possibility ofany injury to the apparatus during manual raising of the recockingmechanism, a mechanically operable, normally closed valve 408 ispositioned to be actuated by a finger 410 carried by the recockingmechanism. The arrangement is such that the finger 410 is adapted toactuate and open the normally closed valve 408 when the recockingmechanism has reached its uppermost position. The valve 408 has one portconnected by a conduit 412 with the pressure line 296, and another portconnected by a drain line 414 with the reservoir.

It is contemplated that there are many instances in which it may bedesirable to release the ram from a position beneath its normal fullyraised or uppermost position. Thus, the control circuit is providedwithmeans whereby the ram may be manually lowered to the desiredintermediate position or even to its lowermost position. This meansincludes a switch in the control panel 281 manually operable by a pushbutton 416 and suitably connected by wires 418 and 420 with the solenoid286. When the button 416 is depressed, the solenoid 286 is energized forshifting the valve 282 in a manner which causes the pressure inlet port288 to be connected with the port 306 while the port 292 is connectedwith the drain port 312. This causes fiuid under pressure to be directedto the check valve actuating devices 302 and 304 for opening the checkvalves 298 and 300 and permitting fluid to flow from the cylinders 162and 164 through the check valves 298 and 300 and back to the reservoirin order to lower the recocking mechanism and thus the ram.

While the preferred embodiment of the present invention has been shownand described herein, it is obvious that many details may be changedwithout departing from the spirit and scope of the appended claims.

The invention is claimed as follows:

1. A machine of the type described, comprising a onepiece completelymetal frame including a head portion, a

relatively heavy base portion spaced from said head portion and sideelements extending from said head portion and having integral junctionswith said base portion, a ram disposed for reciprocal movement betweensaid head I and base portions, sealed high pressure pneumatic means onsaid head portion for actuating said ram through a working stroke at ahigh Velocity and directing the ram against a workpiece with a highimpact force, means for recocking and releasably retaining said ramincluding a latch structure mounted for movement along said framebetween said head and base portions, means for actuating said latchstructure between said head and base portions, said base portionincluding a rounded seat oppositely from said ram and substantiallymerging with said junctions, and a metal pad member separate from andsubstantially complementary to and fitting within said seat forsupporting a workpiece to be processed and for distributing impact loadsacross said base portion in a manner which minimizes stressconcentrations at said junctions.

2. A machine, as defined in claim 1, wherein said means for actuatingsaid ram comprises a spherical pressure chamber, said ram including anelongated portion siidably extending into said chamber.

3. A machine, as defined in claim 1, wherein said seat and said padmember have a semicylindrical configuration.

4. A machine of the type described, comprising a metal main framecomprising a hollow head portion providing a high pressure pneumaticchamber, a relatively heavy base portion spaced from said head portion,and a plurality of side elements extending from said head portion andhaving junctions with said base portion, a ram telescopically associatedwith and extending into said pressure chamber for actuation by fluidpressure therein at a high velocity through a working stroke between acooked position and an extended position, said base portion including agenerally semicylindrical seat oppositely from said ram andsubstantially merging with said junctions, a substantiallysemicylindrical metal pad member separate from and complementary to andremovably fitting within said seat for supporting a workpiece to beprocessed and for distributing impact loads across said base portion,and means for recocking and releasably retaining said ram at the cockedposition including latch means releasably engageable with the ram andextended positions, and means for actuating said latch means betweensaid cocked and extended positions and connected with and supportingsaid latch means from said main frame while the latch means is engagedwith the ram and is moving toward or retained at said cocked positionand for effectively disconnecting said latch means from said main framewhile said ram is moving through its work stroke.

5. A machine of the type described, comprising a one piece main frameincluding a hollow head portion providing a pressure chamber, arelatively heavy base portion spaced from said head portion, and aplurality of side elements extending from said head portion and havingintegral junctions with said base portion, a ram telescopicallyassociated with and extending into said pressure chamber for actuationby fluid pressure therein at a high velocity through a working stroke,said base portion including a generally semi-cylindrical seat oppositelyfrom said ram and substantially merging of said junctions, and asubstantially semi-cylindrical pad member complementary to and fittingwithin said seat for supporting a workpiece to be processed and fordistributing impact loads across said base portion, said ram beingmovable between a retracted and cocked position and an extendedposition, said machine including means for returning said ram to andreleasably retaining the ram in said cocked position, said cocking andretaining means comprising a cocking frame shiftable along said firstmentioned frame between said extended and cocked positions, means onsaid cocking frame for releasably engaging the ram, means on saidcocking frame for releasably locking said ram engaging means, and meansfor actuating said cocking frame between the extended and cockedpositions and for supporting said cocking frame on said first mentionedframe while the ram is being moved toward and retained in said cockedposition and for effectively disconnecting said cocking frame from saidfirst mentioned frame while said ram is moving during a working stroketoward said extended position.

6. A machine of the type discribed, comprising a main frame includingspaced apart head and base portions and connecting elements extendingbetween said portions, pressure actuating means on said head portion, aram assembled with and operable by said actuating means through a workstroke between extended and cocked positions, and means for recockingand releasably retaining said ram including a cocking frame mounted formovement along said main frame between said cooked and extendedpositions, latch means on said cocking frame for releasably engaging andretaining said ram, releasable locking means for preventing accidentalrelease of said latching means, and means for actuating said cockingframe between said cocked and extended positions.

7. A machine, as defined in claim 6, which includes a plurality of saidlatch means spaced around said ram and a plurality of said locking meansrespectively associated with said latch means, and means forsequentially actuating and releasing said locking means and thensimultaneously actuating all of said latch means for releasing the ram.

8. A machine, as defined in claim 6, wherein said latch means comprisinga pivotally supported member, a roller element on said pivotallysupported member engageable beneath a portion of said ram, and means forshifting the pivotally supported member for selectively engaging saidroller element with and disengaging the roller element from said ram.

9. A machine as defined in claim 8, wherein said latch means includesfluid pressure actuated means connected with said pivotally mountedmember for operating the pivotally supported member for engaging theroller element with the ram,

10. A machine, as defined in claim 6, wherein said means for actuatingsaid cocking frame between said cocked and extended positions includescomplementary fluid cylinder and piston means acting between saidcocking frame and said main frame for shifting the cocking frame towardand releasably retaining the cocking frame at said cocked position, oneof said last named means being connected to one of said frames and theother of said last named means being axially shiftably connected to theother of said frames, means limiting axial movement in one directionbetween said other of said last named means and said other frame whilepermitting such relative movement in an opposite direction forsupporting said cocking frame while the ram is being shifted toward orretained in said cocked position and for effectively disconnecting saidcocking frame from said main frame during movement of the ram throughits Working stroke.

11. A machine of the type described, comprising a main frame includingspaced apart head and base portions and connecting elements extendingbetween said portions, a ram movable through a working stroke betweensaid portions and to and from extended and cocked positions, pressuremeans on said head portion for actuating said ram through said workingstroke, and means for recocking and releasably retaining said ramincluding a latch structure mounted for movement along said main framebetween said cocked and extended positions, means for actuating saidlatch structure between said cocked and extended positions, said latchstructure comprising a pivotally mounted member, a roller element onsaid pivotally mounted member and engageable beneath a portion of saidram, and means for shifting said pivotally mounted member for engagingsaid roller element and disengaging the roller element from said ram.

12. A machine, as defined in claim 11, wherein said roller elementcomprises a plurality of circumferentially spaced recesses substantiallycomplementary to and adapted to receive a marginal portion of the ram.

13. A machine of the type described, comprising a main frame includingspaced apart head and base portions and connecting elements extendingbetween said portions, a ram movable through a work stroke toward saidbase portion and between extended and cocked positions, fluid pressuremeans on said head portion for actuating said ram through said workstroke, and means for recocking and releasably retaining said ram at thecocked position including latch means releasably engageable with the ramand mounted for movement along said main frame between said cocked andextended positions, and means for actuating said latch means betweensaid cocked and extended position and connected with and supporting saidlatch means from said main frame while the latch means is engaged withthe ram and is moving toward or retained at said cocked position and foreffectively disconnecting said latch means from said main frame whilesaid ram is moving through its work stroke.

14. A machine, as defined in claim 13, which includes motion arrestingmeans connected between said latch means and anchored separately fromsaid main frame for arresting motion which may be imparted to the latchmeans as a result of reaction forces created upon movement of the ramthrough its working stroke.

15. A machine, as defined in claim 13, wherein said means for recockingand releasably retaining the ram comprises a cocking frame supportingsaid latch means and mounted for movement along said main frame betweensaid cocked and extended positions, and said means for actuating andsupporting said latch means from and disconnecting the latch means withrespect to the main frame comprises complementary fluid cylinder andpiston means acting between said cocking frame and said main frame.

16. A machine, as defined in claim 15, which includes means forintroducing hydraulic fluid under pressure into said cylinder means foractuating the cylinder means for moving said cocking frame toward andretaining the cocking frame in said cocked position, and means forrelieving the pressure of said hydraulic fluid substantially immediatelyupon the start of downward movement of the ram.

17. A machine, as defined in claim 15, wherein said cylinder means isfixed with respect to said cocking frame, said piston means includes apassageway therethrough for accommodating How of hydraulic fluid intoand out of said cylinder means, and said machine including coupling 10means having a sliding connection with said piston means and supportedseparately from both of said frames for connecting the piston means witha source of hydraulic fluid.

References Cited in the file of this patent UNITED STATES PATENTSShipway Jan. 26, 1904 Irvine Feb. 11, 1913 Schneider May 1, 1934Myercord et a1 Apr. 30, 1935 Oeckl et al. June 20, 1939 Chapman Oct. 3,1939 Fitzgerald et a1. Oct. 29, 1940 Steinfort et al Dec. 9, 1958Kandall et al. Dec. 1, 1959 Smith Nov. 28, 1961 Ottestad et a1. May 29,1962

1. A MACHINE OF THE TYPE DESCRIBED, COMPRISING A ONEPIECE COMPLETELYMETAL FRAME INCLUDING A HEAD PORTION, A RELATIVELY HEAVY BASE PORTIONSPACED FROM SAID HEAD PORTION AND SIDE ELEMENTS EXTENDING FROM SAID HEADPORTION AND HAVING INTEGRAL JUNCTIONS WITH SAID BASE PORTION, A RAMDISPOSED FOR RECIPROCAL MOVEMENT BETWEEN SAID HEAD AND BASE PORTIONS,SEALED HIGH PRESSURE PNEUMATIC MEANS ON SAID HEAD PORTION FOR ACTUATINGSAID RAM THROUGH A WORKING STROKE AT A HIGH VELOCITY AND DIRECTING THERAM AGAINST A WORKPIECE WITH A HIGH IMPACT FORCE, MEANS FOR RECOCKINGAND RELEASABLY RETAINING SAID RAM INCLUDING A LATCH STRUCTURE MOUNTEDFOR MOVEMENT ALONG SAID FRAME BETWEEN SAID HEAD AND BASE PORTIONS, MEANSFOR ACTUATING SAID LATCH STRUCTURE BETWEEN SAID HEAD AND BASE PORTIONS,SAID BASE PORTION INCLUDING A ROUNDED SEAT OPPOSITELY FROM SAID RAM ANDSUBSTANTIALLY MERGING WITH SAID JUNCTIONS, AND A METAL PAD MEMBERSEPARATE FROM AND SUBSTANTIALLY COMPLEMENTARY TO AND FITTING WITHIN SAIDSEAT FOR SUPPORTING A WORKPIECE TO BE PROCESSED AND FOR DISTRIBUTINGIMPACT LOADS ACROSS SAID BASE PORTION IN A MANNER WHICH MINIMIZES STRESSCONCENTRATIONS AT SAID JUNCTIONS.